EP1959131B1 - Eolienne dotée d'un frein de rotor actionné hydrauliquement - Google Patents

Eolienne dotée d'un frein de rotor actionné hydrauliquement Download PDF

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Publication number
EP1959131B1
EP1959131B1 EP07020758A EP07020758A EP1959131B1 EP 1959131 B1 EP1959131 B1 EP 1959131B1 EP 07020758 A EP07020758 A EP 07020758A EP 07020758 A EP07020758 A EP 07020758A EP 1959131 B1 EP1959131 B1 EP 1959131B1
Authority
EP
European Patent Office
Prior art keywords
pressure
brake
wind turbine
valve
turbine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07020758A
Other languages
German (de)
English (en)
Other versions
EP1959131A2 (fr
EP1959131A3 (fr
Inventor
Christian Wedekind
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nordex Energy SE and Co KG
Original Assignee
Nordex Energy SE and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nordex Energy SE and Co KG filed Critical Nordex Energy SE and Co KG
Priority to PL07020758T priority Critical patent/PL1959131T3/pl
Publication of EP1959131A2 publication Critical patent/EP1959131A2/fr
Publication of EP1959131A3 publication Critical patent/EP1959131A3/fr
Application granted granted Critical
Publication of EP1959131B1 publication Critical patent/EP1959131B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/0244—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/0244—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for braking
    • F03D7/0248—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for braking by mechanical means acting on the power train
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/90—Braking
    • F05B2260/902—Braking using frictional mechanical forces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2270/00—Control
    • F05B2270/50—Control logic embodiment by
    • F05B2270/506—Control logic embodiment by hydraulic means, e.g. hydraulic valves within a hydraulic circuit
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present invention relates to a wind energy plant with a hydraulically actuated rotor brake.
  • wind turbines have a rotor brake in the drive train.
  • the rotor brake is usually arranged behind the transmission and used in wind turbines with an active blade angle adjustment as an additional braking system through which the rotor is held in its position when the wind turbine is stopped.
  • the brake system is designed as a passive brake or as a so-called fail-safe brake.
  • the braking torque of the passive brake is achieved via a spring assembly that biases the associated brake shoes into the braking position.
  • the thereby applied braking torque is generated by the force exerted by the spring elements spring force. It is therefore necessary to provide for a wind turbine, which requires a strong braking torque, correspondingly large spring assemblies in the brake.
  • the passive rotor brake described above is achieved by, for example, a hydraulic fluid is introduced into the brake cylinder.
  • the hydraulic fluid is introduced into the brake cylinder such that its pressure acts against the force of the spring assembly.
  • active brakes for wind turbines are known in which the braking torque is not applied via a spring element, but also increases the braking torque with increasing hydraulic pressure.
  • the advantage of an active brake is that it builds smaller and is much cheaper. Also, a significantly greater braking torque is possible with an active brake.
  • a braking device for a wind turbine in which a brake valve assembly comprises a 3/2-way seat valve, via which the pressure chamber is connected for braking with a pressure medium source and for releasing the brake with a pressure medium sink. Furthermore, it is known to provide a compensating accumulator and a hydraulic accumulator on the supply line to the brake cylinder.
  • the invention has for its object to provide a hydraulically operated device which compensates by simple means pressure fluctuations which occur during braking with a clamped volume of hydraulic fluid.
  • the wind turbine according to the invention is equipped with a hydraulically actuated rotor brake for a drive train.
  • the rotor brake has at least one hydraulically actuated brake cylinder whose braking torque increases with increasing hydraulic pressure.
  • the rotor brake is an active rotor brake.
  • a hydraulic accumulator is provided with hydraulic fluid, which is connected to a pressure line, via which a brake pressure of the hydraulic fluid is applied to the brake cylinder during braking of the drive train.
  • the memory according to the invention is provided to compensate for pressure fluctuations in the pressure line during the braking process, in which the brake pressure applied to the brake cylinder.
  • brake pressure is smaller than the pressure applied to the brake cylinder during the holding process (holding pressure).
  • the invention provides excluding the memory during braking. This means that the memory is provided only with a significantly lower pre-charge pressure than a memory which is also dimensioned to bear the holding pressure. Thus, a smaller memory size can be used in the wind turbine according to the invention.
  • a first pressure-reducing valve which reduces an applied system pressure to the brake pressure.
  • the memory according to the invention is connected to a pressure line which connects the output of the first pressure reducing valve with the brake cylinder.
  • the pressure of the hydraulic fluid provided in the reservoir corresponds to the brake pressure of the hydraulic fluid, so that fluctuations in the brake pressure can be compensated.
  • the hydraulics also have a second pressure reducing valve, which reduces the system pressure of the hydraulic fluid to the holding pressure of the hydraulic fluid.
  • the holding pressure of the hydraulic fluid corresponds to the pressure required to produce at least the necessary holding torque on the brake cylinder. Due to the lower coefficient of friction of the mating brake linings and brake disc in the cold state, the holding pressure at standstill of the drive train is higher than the brake pressure.
  • the outgoing from the pressure reducing valves pressure lines via a switching valve with either a pressure line to the brake cylinder can be connected.
  • a switching unit is provided, which controls the switching valve to the first or second pressure reducing valve to connect to the brake cylinder. The switching unit determines when the pressure of the first pressure reducing valve and when the pressure of the second pressure reducing valve is applied to the brake cylinder.
  • the switching unit controls the switching valve hydraulically. But it is also possible that the switching unit controls the switching valve electrically.
  • the pressure line to the brake cylinder via a 2/2-way valve is connected to a tank. By opening the 2/2-way valve, the pressure can be released from the brake cylinder and the brake cylinder opens.
  • a pressure system is provided, which provides fail-safe hydraulic fluid in sufficient quantity available.
  • the single FIGURE shows a schematic view of a hydraulic system for controlling a rotor brake.
  • a pressure system 10 provides a hydraulic fluid at a system pressure p s .
  • the printing system 10 can also supply other hydraulic consumers of the wind power plant via further pressure lines 12.
  • a hydraulically actuated pitch system may be provided in the wind turbine.
  • the pressure system feeds a first pressure line 14, in which a 2/2-way valve is arranged.
  • the 2/2-way valve 16 is mechanically biased in its open position. Electrically, the 2/2-way valve can be placed in a locked position in which a pressure in the pressure line 18 is maintained.
  • the pressure line 18 forks and opens into a first pressure reducing valve 20 and connected in parallel to a second pressure reducing valve 22.
  • the first pressure reducing valve 20 reduces the applied system pressure p s to the brake pressure p B.
  • a pressure line 24 is provided with a check valve 26 which prevents the hydraulic fluid from running back into the pressure system 10.
  • the pressure line 24 is connected to a reservoir 28 containing hydraulic fluid.
  • the hydraulic fluid in the reservoir 28 has the brake pressure p B.
  • a second branch with the second pressure-reducing valve 22 is connected in parallel to the above-described branch with the first pressure-reducing valve 20.
  • the system pressure p s is also applied via the pressure line 18.
  • the pressure reducing valve 22 reduces the pressure of the hydraulic fluid to the holding pressure p H , which is necessary to apply the necessary holding torque when the drive train is stationary. As a rule, the holding pressure and the holding torque are greater than the brake pressure and the braking torque of the rotor brake.
  • the output line 30 of the second pressure reducing valve 22 is also provided with a spring-biased check valve 32.
  • Pressure line 24 and 30 open in a first hydraulically piloted 3/2-way valve 34.
  • the first 3/2-way valve switches the holding pressure p H of the pressure line 30 to a pressure line 36, which leads to the brake cylinder 38.
  • the first 3/2-way valve switches the brake pressure p B from the pressure line 24 to the pressure line 36.
  • the pressure line 36 leads to a brake cylinder shown schematically with a brake piston 40.
  • the brake piston 40 is actuated via the introduced hydraulic fluid and exerts a corresponding force on the brake pad of the brake.
  • the pressure line 36 is connected via a further pressure line 42 with a 2/2-way valve 44.
  • the 2/2-way valve locks in its spring-biased position, the pressure line 42.
  • an electric actuator 45 the 2/2-way valve 44 can be switched to its open position and directs the hydraulic fluid in a tank 46. In this way, the brake cylinder 38th relieved and the brake released.
  • a hydraulic switching unit which has a memory 48 for hydraulic fluid.
  • the memory 48 is connected via a control line 50 to the first 3/2-way valve 34.
  • the pressure line 52 has a flow control valve 54 which is connected via the pressure line 56 with a second 3/2-way seat valve 58.
  • the second 3/2-way seat valve 58 is connected in its de-energized position with a tank 60 into which the hydraulic fluid can flow from the reservoir 48.
  • the 3/2-way seat valve connects the pressure line 62 of the pressure system 10 to the reservoir 48 to restore the desired pressure in the reservoir.
  • the pressure in the reservoir 48 reduces with the drainage of the hydraulic fluid from the tank 60.
  • the change-over valve switches between the holding pressure and the brake pressure.
  • the first 3/2-way valve 34 serving as a changeover valve is in the position a.
  • the system pressure is lowered via the pressure reducing valve 20 to the desired brake pressure and the brake cylinder is closed.
  • the damping memory 28 With the help of the damping memory 28, the existing volume in the rotor brake, caused by dimensional tolerances of the brake disc, buffered, the brake pressure remains constant.
  • the damping memory is designed as a hydraulic accumulator known per se, in which a compressible medium is provided for generating the pressure.
  • the first 3/2-way valve 34 is switched and the high holding pressure is applied.
  • the damping memory 24 is thus taken from the pressure system, so that it is not acted upon by the holding pressure.
  • the switching between brake pressure and holding pressure is time-dependent. In the illustrated embodiment, the time to switch is dependent on how long it takes for the hydraulic fluid from the reservoir 48 to fall below a predetermined pressure value. Alternatively, it is also possible to provide an electrical timer for switching.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Wind Motors (AREA)
  • Braking Arrangements (AREA)

Claims (10)

  1. Éolienne avec un frein de rotor actionné hydrauliquement pour une chaîne cinématique, qui comporte au moins un cylindre de frein (38) actionné hydrauliquement dont le couple de freinage augmente avec l'augmentation de la pression hydraulique, un volume de liquide hydraulique étant, lors de l'actionnement du frein, serré par une premier valve de réduction de pression (20) dans le cylindre de frein (38) et dans sa conduite de pression (24, 36),
    un réservoir (28) avec du liquide hydraulique étant prévu, qui est connecté à la conduite de pression (24, 36), et la premier valve de réduction de pression (20) réduisant à la pression de freinage (pB) une pression de système (ps) qui est présente,
    caractérisé par, en plus, une deuxième valve de réduction de pression (22) est prévu qui réduit la pression de système (ps) à la pression d'arrêter (pH).
  2. Éolienne selon la revendication 1, caractérisé par la conduite de pression (24) connecte la premier valve de réduction de pression (20) au cylindre de frein (38).
  3. Éolienne selon la revendication 1 ou la revendication 2, caractérisé par la pression hydraulique dans le réservoir (28) correspond à la pression de freinage (pB).
  4. Éolienne selon la revendication 1, caractérisé par la pression d'arrêter (pH) de la deuxième valve de réduction de pression (22) est supérieure à la pression de freinage (pB) de la premier valve de réduction de pression (20).
  5. Éolienne selon une des revendications 1 à 4, caractérisé par les conduites de pression (24, 30) partant des valves de réduction de pression (20, 22) peuvent être connectées, par le biais d'une valve de commutation (34), de façon alternative à une conduite de pression (36) conduisant au cylindre de frein (38).
  6. Éolienne selon la revendication 5, caractérisé par le réservoir (28) est, dans une position de la valve de commutation, séparé du cylindre de frein.
  7. Éolienne selon la revendication 5 ou la revendication 6, caractérisé par il est prévu un matériel de commutation qui commande la valve de commutation (34) afin de connecter la premier ou la deuxième valve de réduction de pression au cylindre de frein.
  8. Éolienne selon la revendication 7, caractérisé par le matériel de commutation contrôlé la valve de commutation (34) hydrauliquement ou électriquement.
  9. Éolienne selon une des revendications 1 à 8, caractérisé par la conduite de pression (36) conduisant au cylindre de frein (38) est connectée à un tank par le biais d'un valve 2/2 voies (44).
  10. Éolienne selon une des revendications 1 à 9, caractérisé par, pour les conduites de pression, il est prévu un système à pression (10) qui met à disposition le liquide hydraulique surement devant une panne.
EP07020758A 2007-01-10 2007-10-24 Eolienne dotée d'un frein de rotor actionné hydrauliquement Not-in-force EP1959131B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL07020758T PL1959131T3 (pl) 2007-01-10 2007-10-24 Elektrownia wiatrowa z uruchamianym hydraulicznie hamulcem wirnika

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007002137A DE102007002137A1 (de) 2007-01-10 2007-01-10 Windenergieanlage mit einer hydraulisch betätigten Rotorbremse

Publications (3)

Publication Number Publication Date
EP1959131A2 EP1959131A2 (fr) 2008-08-20
EP1959131A3 EP1959131A3 (fr) 2010-07-14
EP1959131B1 true EP1959131B1 (fr) 2012-07-11

Family

ID=39509845

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07020758A Not-in-force EP1959131B1 (fr) 2007-01-10 2007-10-24 Eolienne dotée d'un frein de rotor actionné hydrauliquement

Country Status (4)

Country Link
US (1) US7494193B2 (fr)
EP (1) EP1959131B1 (fr)
DE (1) DE102007002137A1 (fr)
PL (1) PL1959131T3 (fr)

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CN103899484A (zh) * 2014-04-17 2014-07-02 上海电机学院 一种风电机组刹车装置及刹车方法

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Publication number Priority date Publication date Assignee Title
CN103899484A (zh) * 2014-04-17 2014-07-02 上海电机学院 一种风电机组刹车装置及刹车方法
CN103899484B (zh) * 2014-04-17 2017-03-08 上海电机学院 一种风电机组刹车装置及刹车方法

Also Published As

Publication number Publication date
PL1959131T3 (pl) 2012-12-31
EP1959131A2 (fr) 2008-08-20
US20080164751A1 (en) 2008-07-10
DE102007002137A1 (de) 2008-07-17
US7494193B2 (en) 2009-02-24
EP1959131A3 (fr) 2010-07-14

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